WO1997005410A1 - Ratio selector mechanisms - Google Patents

Ratio selector mechanisms Download PDF

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Publication number
WO1997005410A1
WO1997005410A1 PCT/GB1996/001732 GB9601732W WO9705410A1 WO 1997005410 A1 WO1997005410 A1 WO 1997005410A1 GB 9601732 W GB9601732 W GB 9601732W WO 9705410 A1 WO9705410 A1 WO 9705410A1
Authority
WO
WIPO (PCT)
Prior art keywords
ratio
actuator
valve
pressure
mechanism according
Prior art date
Application number
PCT/GB1996/001732
Other languages
English (en)
French (fr)
Inventor
John Spooner
Mark Stanley Willows
David Anthony Harries
Original Assignee
Ap Kongsberg Holdings Limited
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from GBGB9515333.4A external-priority patent/GB9515333D0/en
Priority claimed from GBGB9602734.7A external-priority patent/GB9602734D0/en
Application filed by Ap Kongsberg Holdings Limited filed Critical Ap Kongsberg Holdings Limited
Priority to EP96924999A priority Critical patent/EP0782675B1/de
Priority to JP9507313A priority patent/JPH10507256A/ja
Priority to DE69616259T priority patent/DE69616259T2/de
Priority to US08/809,997 priority patent/US5836207A/en
Priority to GB9705270A priority patent/GB2308413B/en
Publication of WO1997005410A1 publication Critical patent/WO1997005410A1/en

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F16H61/0403—Synchronisation before shifting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/2807—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted using electric control signals for shift actuators, e.g. electro-hydraulic control therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02—Selector apparatus
    • F16H59/08—Range selector apparatus
    • F16H2059/082—Range selector apparatus with different modes
    • F16H2059/084—Economy mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02—Selector apparatus
    • F16H59/08—Range selector apparatus
    • F16H2059/082—Range selector apparatus with different modes
    • F16H2059/085—Power mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02—Selector apparatus
    • F16H59/08—Range selector apparatus
    • F16H2059/082—Range selector apparatus with different modes
    • F16H2059/087—Winter mode, e.g. to start on snow or slippery surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68—Inputs being a function of gearing status
    • F16H2059/6807—Status of gear-change operation, e.g. clutch fully engaged
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H2061/2823—Controlling actuator force way characteristic, i.e. controlling force or movement depending on the actuator position, e.g. for adapting force to synchronisation and engagement of gear clutch
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/36—Inputs being a function of speed
    • F16H59/44—Inputs being a function of speed dependent on machine speed of the machine, e.g. the vehicle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68—Inputs being a function of gearing status
    • F16H59/70—Inputs being a function of gearing status dependent on the ratio established
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/68—Inputs being a function of gearing status
    • F16H59/72—Inputs being a function of gearing status dependent on oil characteristics, e.g. temperature, viscosity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/40—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism comprising signals other than signals for actuating the final output mechanisms
    • F16H63/46—Signals to a clutch outside the gearbox
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19251—Control mechanism

Definitions

  • This invention relates to ratio selector mechanisms and in particular to such mechanisms for the selection of the operative ratio in a vehicle transmission.
  • a selector mechanism of the type specified in which the operating pressure of the actuating means is varied during selection of a given ratio in the associated transmission or dependant on the ratio being selected in the associated transmission.
  • the operating pressure may be lowered when selecting the higher ratios of the associated transmission.
  • the actuating means comprises a first fluid pressure operated actuator which moves a selector member in a first direction to engage one of a number of ratio shift rails and a second fluid pressure operated actuator which moves the selector member in a second direction to longitudinally displace the engaged shift rail to engage an associated selected ratio.
  • the level of fluid pressure applied to the second actuator may be varied dependent on the position of the first actuator.
  • the pressure applied to the second actuator (which determines the force used in actually engaging the selected ratio) can be lowered when the first actuator is in engagement with the selector rail(s) associated with the higher ratios of the associated vehicle transmission.
  • This is particularly advantageous in synchromesh transmissions where the synchromesh units associated with the higher ratios are normally of a smaller diameter and therefore less powerful as they have a small speed differential to accommodate.
  • the level of pressure supplied to the second actuator may be controlled by a valve member which acts against a bias force which is varied in dependence on the position of the fir ⁇ t actuator.
  • the above arrangement can be provided by an abutment which moves with the first actuator and which bears on a spring which biases the valve member toward ⁇ a closed position, movement of the first actuator thus varying the effective bias force of the spring.
  • pressure is supplied to the actuating means via a master control valve which operates as a solenoid-operated proportional pressure regulating valve which outputs fluid at a pressure proportional to a signal (solenoid current) issued to an electronic control means in accordance with predetermined transmission or vehicle operating criteria.
  • the master control valve may be a solenoid-operated proportional flow valve and a pressure transducer is provided which sense ⁇ the pressure level supplied to the actuating means and whose output is fed to an electronic control means which issues signals to the solenoid of the master control valve to control the actuating means pressure in accordance with predetermined transmissin or vehicle operating criteria.
  • the shift load may be arranged to be lower up to the point at which the synchronising components come into contact and then higher to actually achieve synchronisation.
  • the pres ⁇ ure supplied to the actuators can easily be varied at any point in a shift cycle by varying the signal applied to the master control valve.
  • FIG. 1 diagrammatically illustrates a vehicle transmission ratio selector mechanism in accordance with the present invention
  • Figure 2 shows a ratio selection gate and associated shift rails used in the mechanism of figure 1;
  • Figure 3 diagrammatically illustrates a ball-type fluid pressure reducing valve which forms part of the selector mechanism
  • Figure 4 shows graphically the operating characteristic of the pressure reducing valve of figure 3;
  • Figure 5 shows graphically the operating characteristic of an alternative pressure limiting valve
  • Figure 6 shows diagrammatically a suitable form of pres ⁇ ure limiting valve
  • Figure 7 diagrammatically illustrates the basic constructional details of an alternative spool-type pressure control valve
  • Figure 8 diagrammatically illustrates an alternative vehicle transmission ratio selector mechanism in which actuator pressure is controlled by an electronically controlled proportional pressure regulating valve
  • Figure 9 diagrammatically illustrates a further vehicle transmission ratio selector mechanism in which actuator pressure is controlled by electronically controlled proportional flow valves and an associated pressure transducer, and
  • Figure 10 is a flow chart of the decision process used to control the mechanism of Figure 9.
  • FIG 1 this shows diagrammatically a gear selector mechanism in accordance with the present invention in which a selector member 10 is engageable with three shift rails 11,12 and 13 which engage ratios in an associated vehicle transmission using the shift gate shown in figure 2.
  • the shift rail 11 engages ratios 1 and 2
  • shift rail 12 engages ratios 3 and 4
  • shift rail 13 engages ratio 5 and reverse.
  • the selector member 10 is movable in a first direction X by a first fluid pressure operated actuator 14 and in a second direction Y by a second fluid pres ⁇ ure operated actuator 15. Thu ⁇ by a combination of the movements of the first and second actuators 14 and 15 the selector member 10 can be engaged with the required shift rail 11,12 or 13 and move in direction Y to engage the de ⁇ ired ratio associated with the currently engaged shift rail.
  • the actuators 14 and 15 each comprise a double-acting ram with an operating rod 14a and 15a respectively which is operatively connected with the selector member 10.
  • the presence of the operating rods 14a and 15a results in piston 16 of actuator 14 having a rod side effective area which is less than the effective area of the other head side of the piston.
  • piston 17 of actuator 15 has a smaller rod side area. Thus if both sides of the pistons are subjected to the same fluid pressure the piston ⁇ 16 and 17 will be di ⁇ placed along the actuators to extend the associated operating rods 14a and 15a.
  • Valve 20 is a master on/off valve which receives pressuri ⁇ ed fluid from a pump 23. Ma ⁇ ter valve 20, when in its on condition, supplies fluid to proportional flow valves 21 and 22 and also to the rod-end of each actuator 14 and 15.
  • a pressure regulating valve 24 is provided in the connection between master valve 20 and the rod end of actuator 15. The operation of pressure reducing valve 24 will be described in detail below.
  • Master valve 20 and proportional flow valves 21 and 22 are all controlled from an electronic control unit 25 which not only issues electrical control signal ⁇ to the solenoids 20a,21a and 22a of the valves but received signal inputs from potentiometers 26 and 27 which indicate the po ⁇ ition of a ⁇ sociated operating rods 14a and 15a and also a signal from a sensor 28 associated with a ratio selector lever 29 which is moved within the ratio selection gate ⁇ hown in figure 2 to ⁇ elect the desired ration of the associated transmission.
  • the sensor (or sensors) 28 outputs a signal to control unit 25 which is processed by control unit 25 and results in the emission of a signal to master valve 20 to move to the "on" position in.which pressuri ⁇ ed fluid i ⁇ ⁇ upplied to valve ⁇ 21 and 22 and al ⁇ o to the rod end of both actuator ⁇ 14 and 15.
  • valves 21 and 22 are operated by the control unit 25 in the appropriate sequence to give the appropriate movement of operating rods 14a and 15a in the appropriate sequence.
  • the fluid pres ⁇ ure ⁇ upplied to actuator 15, which moves the shift rail ⁇ 11,12 and 13 in direction Y to actually engage the ⁇ elected ratio, is varied dependent on which shift rail is engaged by the selector member 10.
  • Thi ⁇ variation in applied pressure is achieved by the previously referred to pressure reducing valve 24.
  • operating rod 14a has an abutment 30 connected therewith which moves with the operating rod.
  • This abutment provides the reaction surface against which a pressure level control spring 31 acts.
  • Pressure reducing valve 24 includes a movable piston member 32 which is acted upon by control spring 31 and within which a ball valve 33 is bia ⁇ ed again ⁇ t a seat 34 provided on the pi ⁇ ton member 32 by a ⁇ pring 35.
  • the end of bore 36 within which piston member 32 slides is provided with a projection 37 which extends through seat 34 to unseat ball valve 33 and piston 32 is held away from the end of bore 36 by spacers 32a on the piston.
  • valve 33 With the valve 24 in the position shown in figure 3, ball valve 33 is unseated and pres ⁇ ure i ⁇ free to flow from master valve 20 via inlet port 38 chamber 39 drilling 40 valve seats 34 and outlet port 41 to the rod end of actuator 15.
  • any further increase in the pressure supplied to the rod end of actuator is in accordance with the area ratio (al-a2)/al and is ⁇ hown as the gradient ⁇ in figure 4 which is a graphical representation of the pressure characteristics of valve 24.
  • valve 24 can be de ⁇ igned a ⁇ a pre ⁇ ure limiting valve in which after the initial closure of the valve there is no further increase in level of pressure ⁇ upplied to the rod end of actuator 15.
  • a valve operating characteristic is shown in figure 5 and can most easily be achieved by modifying the valve of figure 3 to the arrangement shown diagrammatically in figure 6 in which the effect of the pressure in chamber 39 is neutral on the displacement of piston 32 due to the balanced nature of the annular areas A exposed to the pressure in chamber 39.
  • a spool-valve arrangement as shown diagrammatically in figure 7, could be used in which spring 31 act ⁇ on one end of a spool member 50.
  • Edge 51 of an annular groove 52 in spool 50 cooperates with inlet port 38 to cut-off the flow of fluid along drilling 53 in spool 50 when the pressure applied to the outlet end 54 of spool 50 has risen to a level sufficient to displace spool 50 to the right against the action of spring 31.
  • the spool-valve arrangement shown in figure 7 operates as a pressure limiting valve in view of the balanced nature of the groove 52 of the spool.
  • the selector mechanism of the present invention has been described above in relation to a transmi ⁇ sion in which the ratio selection is done manually by the vehicle operator moving a ratio selector lever and, by implication, manually operating an associated drive line clutch, it will be appreciated that the present invention is also applicable to semi-automatic transmission of the type described, for example in the Applicant' ⁇ earlier European patents Nos. 0038113,0043660,0059035 and 0101220 in which the ratio ⁇ are manually ⁇ elected by the operator and the clutch i ⁇ operated by an electro-hydraulic control system.
  • the invention is also applicable to fully automated transmi ⁇ sions of the type described for example, in the Applicant's earlier co-pending UK patent application No. 95 02140.8.
  • Figure 8 shows diagrammatically a selector mechanism (for use with a fully automated transmi ⁇ ion) in which component ⁇ similar in function to the components of figure 1 have been similarly numbered.
  • the master valve 20 shown in Figure 8 is not a simple on/off valve, as in Figure 1, but a solenoid-operated proportional pressure regulating valve which outputs fluid at a pressure proportional to the applied solenoid current.
  • the pressure applied to the head ends of actuators 14 and 15 can be varied either in a manner dependant on the gear ratio being selected or at any point in the selection cycle to provide full control over the pressure exerted by the actuators.
  • the selector mechanism shown in Figure 8 is not only capable of reducing the pressure supplied to the actuator 15 when selecting a higher ratio of the transmi ⁇ sion (as described in the system shown in Figure 1) but is also capable of controlling the level of fluid pressure applied to both actuators in accordance with additional criteria such as : -
  • D) a requirement to vary shift load at different points in a given shifting cycle.
  • the shift load may be arranged to be lower up to the point at which the synchronising components come into contact and then higher to actually achieve synchronisation.
  • the system ⁇ hown in figure 8 also provides control over the vehicle clutch 60 to provide a fully automated transmis ⁇ ion.
  • Valve 63 is controlled by a solenoid 63a from electronic control unit 25 and has position 63a in which flow of fluid to and from the actuator 61 is cut off, position 63b in which the actuator is ⁇ upplied with pre ⁇ surised fluid from pump 23, position 63c in which the pressure in actuator 61 is vented back to sump, and position 63d in which the venting back to ⁇ ump is via a restriction to provide a slow engagement of the clutch. Position 63d is automatically assumed in the event of an electrical/electronic failure to ensure a slow engagement of the clutch which is the default condition of the system.
  • the control system also includes an accumulator 64, electric motor 65 which drives pump 23 and a pressure switch 66 which opens to turn off the pump when the accumulator pressure reaches a predeternined level.
  • the operating position of clutch actuator 61 is fed back as an input to the electronic control unit 25 from a sensor 67.
  • Figure 9 show ⁇ a ⁇ till further form of the present invention which again use ⁇ electronic monitoring of the control valve ⁇ to enable the actuator pre ⁇ ure to be varied at any point in the ratio ⁇ election cycle.
  • components of a similar function to those shown in Figure 1 have been similarly numbered.
  • valve 20 is a master proportional flow valve which receives pressuri ⁇ ed fluid from a circuit which includes pump 23 and an accumulator 75 which is charged via a one way valve 76, with a "blow off" valve 78 to protect from overcharging of accumulator pressure.
  • Master valve 20 supplies fluid to secondary proportional flow valves 21 and 22 and also to the rod-end of each actuator 14 and 15.
  • a pressure transducer 70 is provided in the connection between master valve 20 and the rod end of actuators 14 and 15.
  • Master valve 20 and proportional flow valves 21 and 22 are all controlled from electronic control unit 25 which not only is ⁇ ues electrical control signals to the solenoids 20a,21a and 22a of the valves but received signal inputs from potentiometers 26 and 27 which indicate the position of associated operating rods 14a and 15a and also a ⁇ ignal from a sensor 28 as ⁇ ociated with a ratio selector lever 29 which is moved within the ratio selection gate shown in figure 2 to select the desired ration of the as ⁇ ociated tran ⁇ mission. Addition inputs to control unit 25 are also described below.
  • the sensor (or sensors) 28 outputs a signal to control unit 25 which is processed by control unit 25 and results in the emission of a signal to the solenoid 20a of master valve 20 to supply pressurised fluid to valves 21 and 22 and also to the rod end of both actuators 14 and 15.
  • valves 21 and 22 are operated by the control unit 25 in the appropriate sequence to give the appropriate movement of operating rods 14a and 15a in the appropriate sequence.
  • the master valve 20 and valves 21 and 22 are solenoid-operated proportional flow control valves which output fluid at a flow rate proportional to the applied solenoid current.
  • pre ⁇ ure to the valve ⁇ 21 and 22 can be controlled. If pre ⁇ ure i ⁇ too high, fluid flow into the system is reduced, or vented, so that overall fluid volume in the gear selector mechanism is reduced, and vice versa.
  • the pres ⁇ ure applied to the head end ⁇ of actuators 14 and 15 can be varied either in a manner dependant on the gear ratio being selected or other pre-determined criteria at any point in the selection cycle to provide full control over the pressure exerted by the actuators.
  • the selector mechanism is not only capable of reducing the pres ⁇ ure supplied to the actuator 15 when selecting a higher ratio of the tran ⁇ mission but is also capable of controlling the level of fluid pres ⁇ ure applied to both actuator ⁇ in accordance with additional criteria A) to D) referred to above in relation to Figure 8.
  • Control unit 25 in addition to receiving inputs from sensors 71,72 and 73 also receives information as to the current gear engaged in the transmission from potentiometers 26 and 27 which are associated with shift rails 11,12 and 13 and has memory locations where other operating parameters [such as the loads to which each synchronizer in the transmission should be subjected at each point in it ⁇ operating cycle] are stored.
  • Signals from pressure transducer 70 which are fed back to control unit 25 are used to control the flow openings of valves 20,21 and 22 and hence the pressure applied to actuators 14 and 15 when the system determines that control of the pressure supplied to actuators is required (see deci ⁇ ion box A of Figure 3).
  • box B of Figure 3 a comparison is made between the feedback signal from pres ⁇ ure transducer 70 and the actuator pressure level which the control unit 25 has determined is currently appropriate from all the criteria under consideration.
  • box C and action boxes D and E the appropriate adjustment of fluid flow is made dependant on the result of the current versus appropriate pressure comparison. It is also pos ⁇ ible to use pre ⁇ sure transducer 70 to monitor the pres ⁇ ure currently held in accumulator 75. This removes the need to employ a seperate accumulator pressure monitor. Accumulator pressure can be monitored by transducer 70 when valves 21 and 22 are closed in the so-called "null" position in which no flow ia allowed into or out of actuators 14 and 15 and when the master valve 20 is also fully open.
  • the control unit 25 can be arranged to set-up the above accumulator pressure testing condition on a regular basis when the selector mechanism is not required for the execution of a ratio selection in the associated transmi ⁇ sion.
  • Figure 9 Although the selector mechanism of Figure 9 has been described above in relation to a transmission in which the ratio selection is done manually by the vehicle operator moving a ratio selector lever and, by implication, manually operating an associated drive line clutch, it will be appreciated that the Figure 9 construction is also applicable to semi-automatic transmission of the type described, for example in the Applicant's earlier European patents Nos. 0038113,0043660,0059035 and 0101220 in which the ratios are manually selected by the operator and the clutch is operated by an electro-hydraulic control system. The construction is also applicable to fully automated tran ⁇ mi ⁇ sions of the type described for example, in the Applicant's earlier co-pending UK patent application No. 95 02140.8. For example, the system shown in Figure 9 can also provide control over the associate vehicle clutch to provide a fully automated transmission in the manner described above in relation to Figure 8.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Transmission Device (AREA)
  • Gear-Shifting Mechanisms (AREA)
PCT/GB1996/001732 1995-07-26 1996-07-19 Ratio selector mechanisms WO1997005410A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP96924999A EP0782675B1 (de) 1995-07-26 1996-07-19 Gangschaltvorrichtung
JP9507313A JPH10507256A (ja) 1995-07-26 1996-07-19 比選択機構
DE69616259T DE69616259T2 (de) 1995-07-26 1996-07-19 Gangschaltvorrichtung
US08/809,997 US5836207A (en) 1995-07-26 1996-07-19 Ratio selector mechanisms
GB9705270A GB2308413B (en) 1995-07-26 1996-07-19 Ratio selector mechanisms

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
GB9515333.4 1995-07-26
GBGB9515333.4A GB9515333D0 (en) 1995-07-26 1995-07-26 Ratio selector mechanisms
GBGB9602734.7A GB9602734D0 (en) 1996-02-10 1996-02-10 Ratio selector mechanisms
GB9602734.7 1996-02-10

Publications (1)

Publication Number Publication Date
WO1997005410A1 true WO1997005410A1 (en) 1997-02-13

Family

ID=26307467

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/GB1996/001732 WO1997005410A1 (en) 1995-07-26 1996-07-19 Ratio selector mechanisms

Country Status (8)

Country Link
US (1) US5836207A (de)
EP (2) EP0933564B1 (de)
JP (1) JPH10507256A (de)
KR (1) KR100436278B1 (de)
DE (2) DE69616259T2 (de)
ES (1) ES2166898T3 (de)
GB (1) GB2308413B (de)
WO (1) WO1997005410A1 (de)

Cited By (50)

* Cited by examiner, † Cited by third party
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US6301984B1 (en) 1997-12-19 2001-10-16 Zf Friedrichshafen Ag Gear shifting device
WO1999032809A3 (de) * 1997-12-19 1999-10-07 Zahnradfabrik Friedrichshafen Schalteinrichtung für ein getriebe
WO1999032809A2 (de) * 1997-12-19 1999-07-01 Zf Friedrichshafen Ag Schalteinrichtung für ein getriebe
EP0947743A2 (de) 1998-04-01 1999-10-06 AISIN AI Co., Ltd. Gangschaltvorrichtung für Getriebe
EP0947743A3 (de) * 1998-04-01 2000-06-28 AISIN AI Co., Ltd. Gangschaltvorrichtung für Getriebe
US6131476A (en) * 1998-04-01 2000-10-17 Aisin Ai Co., Ltd. Gear ratio selecting and shifting apparatus in a transmission
WO2000061399A1 (de) 1999-04-14 2000-10-19 Luk Lamellen Und Kupplungsbau Gmbh Kraftübertragungssystem
EP1046341A1 (de) 1999-04-19 2000-10-25 GE.FIN. S.A. Società Finanziaria Fiduciaria Nahrungsmittelzusammensetzung, reich an mehrfachungesättigten Fettsäuren, ihre Herstellung und Verwendung in einer Nahrungsdiät
EP1055546A2 (de) 1999-05-24 2000-11-29 AISIN AI Co., Ltd. Steuereinrichtung und Verfahren zum Schalten von Automatikgetrieben
EP1055546A3 (de) * 1999-05-24 2002-08-21 AISIN AI Co., Ltd. Steuereinrichtung und Verfahren zum Schalten von Automatikgetrieben
US6394929B1 (en) 1999-05-24 2002-05-28 Aisin Ai Co., Ltd. Shift control apparatus and shift control method of automatic transmission
US6276224B1 (en) 1999-05-25 2001-08-21 Aisin Ai Co., Ltd Shift control apparatus for transmission
EP1055847A2 (de) 1999-05-25 2000-11-29 AISIN AI Co., Ltd. Schalteinrichtung für Getriebe
FR2798173A1 (fr) 1999-09-04 2001-03-09 Luk Lamellen & Kupplungsbau Systeme de transmission automatique
DE10037551B4 (de) * 1999-09-11 2012-10-25 Schaeffler Technologies AG & Co. KG Getriebesystem
US6446522B1 (en) 1999-09-11 2002-09-10 Luk Lamellen Und Kupplungsbau Gmbh Automated transmission systems
DE10037547B4 (de) * 1999-09-16 2016-11-24 Schaeffler Technologies AG & Co. KG Automatisiertes Getriebesystem
FR2804194A1 (fr) 2000-01-24 2001-07-27 Luk Lamellen & Kupplungsbau Mecanisme d'enclenchement de rapport
FR2804192A1 (fr) 2000-01-24 2001-07-27 Luk Lamellen & Kupplungsbau Dispositif hydraulique
DE10102031B4 (de) * 2000-03-04 2017-02-09 Schaeffler Technologies AG & Co. KG Getriebe
FR2805877A1 (fr) 2000-03-04 2001-09-07 Luk Lamellen & Kupplungsbau Boites de vitesses
FR2805876A1 (fr) 2000-03-04 2001-09-07 Luk Lamellen & Kupplungsbau Systeme de manoeuvre hydraulique
DE10148083B4 (de) * 2000-10-12 2014-02-13 Schaeffler Technologies AG & Co. KG Hydraulische Betätigungssysteme
US6553857B2 (en) 2000-10-12 2003-04-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic actuation systems
US6637282B2 (en) 2000-11-13 2003-10-28 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic actuation systems
FR2816894A1 (fr) 2000-11-21 2002-05-24 Luk Lamellen & Kupplungsbau Systeme d'actionnement hydraulique
US6568515B2 (en) 2000-11-21 2003-05-27 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic actuation systems
FR2818722A1 (fr) 2000-12-27 2002-06-28 Luk Lamellen & Kupplungsbau Maillon pouvant se conformer
US6810768B2 (en) 2000-12-27 2004-11-02 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Compliant link
US6658951B2 (en) 2001-02-12 2003-12-09 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Hydraulic actuation systems
FR2820694A1 (fr) 2001-02-12 2002-08-16 Luk Lamellen & Kupplungsbau Systeme d'actionnement hydraulique
FR2822513A1 (fr) 2001-03-21 2002-09-27 Luk Lamellen & Kupplungsbau Systemes de transmissions automatisees
GB2378489A (en) * 2001-07-31 2003-02-12 Luk Lamellen & Kupplungsbau Method of gear selection using current pulses in a hydraulic transmission system with actuators and valves
US7275455B2 (en) 2001-09-12 2007-10-02 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Automatic gear system
DE10251031B4 (de) * 2001-11-10 2014-02-27 Schaeffler Technologies AG & Co. KG Kalibrieren eines Fahrzeugsystems
WO2004085886A1 (en) * 2003-03-27 2004-10-07 Ricardo Uk Limited Method for controlling a transmission of a vehicle
US8475336B2 (en) 2009-07-30 2013-07-02 GM Global Technology Operations LLC Hydraulic control system for a dual clutch transmission
US8225687B2 (en) 2009-09-09 2012-07-24 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8403792B2 (en) 2009-10-21 2013-03-26 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8613681B2 (en) 2009-11-19 2013-12-24 GM Global Technology Operations LLC Transmission hydraulic control system having clutch compensator feed override
US8413437B2 (en) 2009-12-08 2013-04-09 GM Global Technology Operations LLC Transmission hydraulic control system having independently controlled stator cooling flow
US8192176B2 (en) 2009-12-10 2012-06-05 GM Global Technology Operations LLC Hydraulic fluid supply system having active regulator
US8443687B2 (en) 2009-12-14 2013-05-21 GM Global Technology Operations LLC Electro-hydraulic control system for a dual clutch transmission
US8402855B2 (en) 2010-01-11 2013-03-26 GM Global Technology Operations LLC Hydraulic control systems for dual clutch transmissions
US8579094B2 (en) 2010-01-11 2013-11-12 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a three path torque converter control subsystem
US8567580B2 (en) 2010-01-22 2013-10-29 GM Global Technology Operations LLC Electro-hydraulic control system for a dual clutch transmission
US8413777B2 (en) 2010-02-17 2013-04-09 GM Global Technology Operations LLC High efficiency hydraulic transmission control system
US8403793B2 (en) 2010-02-17 2013-03-26 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a lubrication regulation valve
US8402993B2 (en) 2010-05-10 2013-03-26 GM Global Technology Operations LLC Hydraulic fluid cooling system for a dual clutch automatic transmission
US8844392B2 (en) 2010-06-09 2014-09-30 Gm Global Technology Operations, Llc Electro-hydraulic and electro-mechanical control system for a dual clutch transmission
US8839928B2 (en) 2010-12-02 2014-09-23 Gm Global Technology Operations, Llc Electro-hydraulic control system for a dual clutch transmission
US8733521B2 (en) 2010-12-06 2014-05-27 Gm Global Technology Operations Apparatus for and method of controlling a dual clutch transmission
US8738257B2 (en) 2010-12-08 2014-05-27 Gm Global Technology Operations, Llc Electro-hydraulic control system and method for a dual clutch transmission
US8942901B2 (en) 2010-12-09 2015-01-27 Gm Global Technology Operations, Llc Method of controlling a hydraulic control system for a dual clutch transmission
US9765885B2 (en) 2010-12-09 2017-09-19 GM Global Technology Operations LLC Method of controlling a hydraulic control system for a dual clutch transmission
US8500600B2 (en) 2011-01-10 2013-08-06 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission having a manual valve with a two gear default strategy
US8915076B2 (en) 2011-01-12 2014-12-23 Gm Global Technology Operations, Llc Transmission hydraulic control system having flow augmentation
US8702548B2 (en) 2011-11-03 2014-04-22 Gm Global Technology Operations Hydraulic control system for an automatic transmission
WO2013068175A1 (de) * 2011-11-11 2013-05-16 Zf Friedrichshafen Ag Verfahren zur steuerung von schaltabläufen eines getriebes
ITBO20120085A1 (it) * 2012-02-22 2013-08-23 Magneti Marelli Spa Servocomando idraulico di un cambio servocomandato
ITBO20120084A1 (it) * 2012-02-22 2013-08-23 Magneti Marelli Spa Servocomando idraulico di un cambio servocomandato
EP2631493A1 (de) * 2012-02-22 2013-08-28 Magneti Marelli S.p.A. Hydraulische Servosteuerung eines servogesteuerten Getriebes
US9574576B2 (en) 2012-02-22 2017-02-21 MAGNETI MARELLI S.p.A. Hydraulic servo-control of a servo-controlled gearbox
EP2631494A1 (de) * 2012-02-22 2013-08-28 Magneti Marelli S.p.A. Hydraulische Servosteuerung eines servogesteuerten Getriebes
US9080666B2 (en) 2012-05-29 2015-07-14 Gm Global Technology Operations, Inc. Discrete mechanism for electronic transmission range selection
US8967351B2 (en) 2012-08-14 2015-03-03 Gm Global Technology Operations, Llc Transmission clutch piston compensator feed circuit
US10167948B2 (en) 2016-03-17 2019-01-01 GM Global Technology Operations LLC Hydraulic control system for an automatic transmission

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DE69616259D1 (de) 2001-11-29
EP0782675A1 (de) 1997-07-09
KR100436278B1 (ko) 2004-07-27
GB2308413A (en) 1997-06-25
GB9705270D0 (en) 1997-04-30
JPH10507256A (ja) 1998-07-14
DE69625937T2 (de) 2003-11-13
DE69625937D1 (de) 2003-02-27
GB2308413B (en) 1999-09-01
EP0782675B1 (de) 2001-10-24
US5836207A (en) 1998-11-17
ES2166898T3 (es) 2002-05-01
EP0933564A3 (de) 1999-10-20
EP0933564B1 (de) 2003-01-22
EP0933564A2 (de) 1999-08-04
KR970706460A (ko) 1997-11-03
DE69616259T2 (de) 2002-07-11

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